Control systems and methods for controlling injection of water into a turbine engine are described. In an exemplary embodiment, the water injection system includes a plurality of nozzles for injecting water into a gas flow through the engine, a water source, a water manifold, a water supply line extending from the water source to the water manifold, a water metering valve for controlling flow through the water supply line, an air manifold, an air flow pipe coupled to the high pressure compressor and to the air manifold, a plurality of air feeder tubes extending from the air manifold to the nozzles, and a plurality of water feeder tubes extending from the water manifold to the nozzles.
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1. A turbine engine comprising:
a low pressure compressor comprising an inlet and an outlet; a high pressure compressor comprising an inlet and an outlet, said high pressure compressor in axial flow relationship with, and downstream from, said low pressure compressor, said high pressure compressor is a multi-stage compressor; a combustor downstream from said high pressure compressor; a high pressure turbine downstream from said combustor; a low pressure turbine in axial flow relationship with, and downstream from, said high pressure turbine; a water injection system comprising: a plurality of nozzles for injecting water into a gas flow through said engine, said nozzles comprising a plurality of long nozzles and short nozzles, said nozzles arranged in alternating configuration such that at least one of said short nozzles is circumferentially intermediate each pair of long nozzles; a water source; a water manifold; a water supply line extending from said water source to said water manifold; a water metering valve for controlling flow through said water supply line; an air manifold; an air flow pipe coupled to all intermediate stage of said high pressure compressor and to said air manifold; a plurality of air feeder tubes extending from said air manifold to said nozzles; an air bleed valve for controlling a size of water droplets discharged from said nozzle; a plurality of water feeder tubes extending from said water manifold to said nozzles. 2. An engine in accordance with
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This application claims the benefit of U.S. Provisional Application No. 60/094,094, filed Jul. 24, 1998.
The United States Government has rights in this invention pursuant to Contract No. DAAH10-98-C-0023.
This invention relates generally to gas turbine engines and more particularly, to prebooster and precompressor water injection in a gas turbine engine.
Gas turbine engines typically include a compressor for compressing a working fluid, such as air. The compressed air is injected into a combustor which heats the fluid causing it to expand, and the expanded fluid is forced through a turbine. The compressor typically includes a low pressure compressor and a high pressure compressor.
The output of known gas turbine engines may be limited by the temperature of the working fluid at the output of the high pressure compressor, sometimes referred to as temperature "T3", and by the temperature of the working fluid in the combustor outlet, sometimes referred to as temperature "T41". To reduce both the T3 and T41 temperatures, it is known to use an intercooler positioned in the fluid flow path between the low pressure compressor and the high pressure compressor. In steady state operation, the intercooler extracts heat from the air compressed in the low pressure compressor, which reduces both the temperature and volume of air entering the high pressure compressor. Such reduction in temperature reduces both the T3 and T41 temperatures. Increased power output therefore can be achieved by increasing flow through the compressor.
Typically, cool water or air circulates through the intercooler, and heat is transferred from the air flow to the cool water or air. The water or air absorbs the heat, and the heated water or air is then removed. Removing the heated water or air results in losses in total cycle thermal efficiency. Therefore, although an intercooler facilitates increased power output, the intercooler reduces thermal efficiency of the engine. The intercooler also introduces pressure losses associated with the removal of air, the actual cooling of that air, and ducting the cooled air to the compressor. Further, it is impractical for an intercooler to also provide interstage cooling.
With at least some known intercoolers, the heated water is removed using a water cooler which dissipates the heated water through a cooling tower as vapor into the environment. Of course, releasing the vapor into the environment raises environmental concerns. Also, a significant amount of water is required by such intercoolers, and such high water consumption increases the operational costs.
It would be desirable to provide a partial increased power output as achieved with intercoolers yet also provide improved thermal efficiency as compared to at least known intercoolers. It also would be desirable to provide increased power output even for single rotor gas turbines.
These and other objects may be attained by a gas turbine engine including prebooster or precompressor water injection which provides many of the same advantages, yet overcomes some shortcomings, of intercooling. In an exemplary embodiment, a gas turbine engine suitable for use in connection with water spray injection includes a low pressure compressor, a high pressure compressor, and a combustor. The engine also includes a high pressure turbine, a low pressure turbine, and/or a power turbine. A water injection apparatus is provided for injecting water into an inlet of the high pressure compressor. The water spray injection apparatus is in flow communication with a water supply, and during engine operation, water is delivered from such supply through the injection apparatus to the inlet of the compressor.
In operation, air flows through the low pressure compressor, and compressed air is supplied from the low pressure compressor to the high pressure compressor. In addition a water spray is supplied to the inlet of the high pressure compressor, and the water spray enters into the high pressure compressor through the inlet. Due to the high temperature environment at the location at which the water spray is injected, the water spray partially evaporates before entering the high pressure compressor. The water spray cools the air flow in the high pressure compressor for at least each stage of compression through which such spray flows, i.e., until it evaporates. Usually about by the mid-stages of the high pressure compressor, and depending on the water quantity, the majority of the water spray is evaporated.
The air and water vapor is further compressed by the high pressure compressor, and the highly compressed air is delivered to the combustor. Airflow from the combustor drives the high pressure turbine the low pressure turbine, and the power turbine. Waste heat is captured by boilers, and heat from the boilers in the form of steam may be delivered to upstream components.
The water spray provides an advantage in that the temperature of the airflow at the outlet of the high pressure compressor (temperature T3) and the temperature of the airflow at the outlet of the combustor (temperature T41) are reduced in steady state operations as compared to such temperatures without the spray. Specifically, the water spray extracts heat from the hot air flowing into and through the high pressure compressor, and by extracting such heat from the air flow, the T3 and T41 temperatures are reduced and compressive horsepower is reduced. The heat is removed as the water vaporizes. Reducing the T3 and T41 temperatures provides the advantage that the engine is not T3 and T41 constrained, and therefore, the engine may operate at higher output levels than is possible without such water spray. That is, with the above described water spray injection and using the same high pressure compressor discharge temperature control limit, the high pressure compressor can pump more air which results in a higher pressure ratio and a higher output.
Set forth below are exemplary configurations of water spray injection in accordance with various embodiments of the present invention. Initially, it should be understood that although specific implementations are illustrated and described, water spray injection can be practiced using many alternative structures and in a wide variety of engines. In addition, and as described below in more detail, water spray injection can be performed at the inlet of a high pressure compressor, at an inlet of the booster, or at both locations.
Water spray injection provides many of the same advantages of intercooling yet overcomes some shortcomings of intercooling. For example, and with intercooling, the heated water (or air) is removed and removal of such heated water (or air) reduces the thermal efficiency of the cycle as well as creates environmental concerns. The significant power increase provided by intercooling typically overcomes the shortcomings associated with intercooling and as a result, intercooling often is utilized when extra power is required using a different or larger airflow booster and a larger high pressure turbine flow function. Water pray injection, as describe below, provides a power increase which may be somewhat less than the maximum power increase provided in a similarly situated intercooler. With water spray injection, however, far less water is utilized and water exits the cycle as water vapor at exhaust gas temperature.
Referring now specifically to the drawings,
In operation, air flows through low pressure compressor 12, and compressed air is supplied from low pressure compressor 12 to high pressure compressor 14. In addition, a water spray is supplied to inlet 26 of high pressure compressor 14, and the water spray enters into compressor 14 through inlet 26. Due to the high temperature environment at the location at which the water spray is injected, the water spray partially evaporates before entering high pressure compressor 14. The water spray cools the air flow in high pressure compressor 14 for at least each stage of compressor 14 through which such spray flows, i.e., until it evaporates. Usually by the sixth stage of compressor 14. the water spray is totally evaporated.
The air is further compressed by high pressure compressor 14, and highly compressed air is delivered to combustor 16. Airflow from combustor 16 drives high pressure turbine 18, low pressure turbine 20, and power turbine 22. Waste heat is captured by boilers 28, 30, and 32, and the waste heat steam is delivered to upstream components coupled to boilers 28, 30 and 32 as described above.
The water particles from water spray apparatus 24 provide the advantage that the temperature of the airflow at the outlet of high pressure compressor 14 (temperature T3) and the temperature of the airflow at the outlet of combustor 16 (temperature T41) are reduced as compared to such temperatures without the spray. Specifically, the water spray extracts heat from the hot air flowing into and through compressor 14, and by extracting such heat from the air flow, the T3 and T41 temperatures are reduced along with the required compressor power. Reducing the T3 and T41 temperatures provides the advantage that engine 10 is not T3 and T41 constrained, and therefore, engine 10 may operate at higher output levels by throttle pushing than is possible without such water spray. In addition to increased power output, water spray injection as described above provides the advantage of less water consumption as compared to intercooling under the same conditions.
Waste heat boilers 70, 72, and 74 are located downstream of power turbine 62. As is known in the art, feed water is supplied to boilers 70, 72, and 74 via a feedwater line 76 which extends through a first stage 78A of intercooler 68, and steam is communicated from boilers 70, 72, and 74 to various upstream components. Particularly, steam from boiler 70 is provided to an inlet 80 of combustor 56, steam from boiler 72 is provided to an inlet of low pressure turbine 60 and an inlet of power turbine 62, and steam from boiler 74 is provided to a last stage of power turbine 62. Except for water spray injection apparatus 64, the various components of turbine 50 are known in the art.
In operation, air flows through low pressure compressor 52, and compressed air is supplied from low pressure compressor 52 to high pressure compressor 54. At least some or all compressed air from low pressure compressor 52 is diverted to flow through a second stage 78B of intercooler 68, and such diverted air is cooled and supplied to inlet 66 of high pressure compressor 54. In addition, a water spray is supplied to inlet 66 of high pressure compressor 54, and the water spray enters into compressor 54 through inlet 66. Due to the higher temperature. environment at the location at which the water spray is injected, the water spray partially evaporates before entering high pressure compressor 54. The water spray cools the air flow in high pressure compressor 54 for at least each stage of compressor 54 through which such spray flows, i.e., until it evaporates. Usually by the sixth stage of compressor 54, the water spray is evaporated.
The air is further compressed by high pressure compressor 54, and highly compressed air is delivered to combustor 56. Airflow from combustor 56 drives high pressure turbine 58, low pressure turbine 60, and power turbine 62. Waste heat is captured by boilers 70, 72, and 74, and the waste heat as steam is delivered to upstream components coupled to boilers 70, 72, and 74 as described above.
By providing a combination of intercooling and water spray injection, it is believed that increased power output is provided by engine 50 as compared to engine 10. Intercooler 68 could take the flow field into the compressor down in temperature to where condensate could appear from ambient humidity. The water spray then could be added into compressor 54 to further reduce T3 at its exit along with reducing its power required to run. However, engine 50 requires more water as compared to engine 10, and engine 50 does dissipate some water to the environment, due to operation of intercooler 68 along with the additional water spray exiting the stack as a vapor at exhaust stack temperature. As compared to the results obtained if only intercooling is used to achieve a power output of engine 50, however, the combination of water spray injection and intercooling results in more water consumption.
Although not shown in the exemplary configuration set forth in
An exemplary configuration of an engine 82 including booster water spray injection is set forth in FIG. 3. The configuration of engine 82 is substantially similar to engine 10 shown in
A dual rotor gas turbine engine 10 is shown schematically in FIG. 5. Engine 160 includes a booster 162 and a power turbine 164 connected by a first shaft 166, a high pressure compressor 168 and a high pressure turbine 170 connected by a second shaft 172, and a combustor 174. Engine 160 further includes pre-booster water spray injection apparatus 176 and pre-compressor water spray injection apparatus 178.
Engine 200 further includes a water injection apparatus 206 for injecting water into an inlet 208 of high pressure compressor 204. Water injection apparatus 206 includes a water metering valve 210 in flow communication with a water manifold 212. Water is supplied to metering valve 210 from a water source or reservoir. Air is supplied to an air manifold 213 from an eight stage bleed 214 of high pressure compressor 204. Bleed 214 serves as a source of heated air. A heat exchanger 216 is coupled to flow pipe or tube 218 which extends from eight stage bleed 214 to air manifold 213. Feeder tubes 220 and 221 extend from air manifold 213 and water manifold 212 to twenty four spray nozzles 222 and 223 radially spaced and extending through outer casing 224. Nozzles 222 are sometimes referred to herein as short nozzles 222, and nozzles 223 are sometimes referred to herein as long nozzles 223. Nozzles 222 and 223 are radially spaced around the circumference of casing 224 in an alternating arrangement as described below in more detail.
Twenty four water feeder tubes 221 extend from water manifold 212, and twenty four air feeder tubes 220 extend from air manifold 213. Each nozzle 222 is coupled to one water feeder tube 221 from water manifold 212 and to one air feeder tube 220 from air manifold 213. Generally, water flowing to each nozzle 222 and 223 is atomized using the high pressure air (e.g., at about 150 psi) taken off eight stage bleed 214 of high pressure compressor 204. The droplet diameter, in this embodiment, should be maintained at about 20 microns. Such droplet diameter is maintained by controlling the rate of flow of water through valve 210 using the water schedule described below in more detail and utilizing the high pressure air from bleed 214. Except for water spray injection apparatus 206, the various components of engine 200 are known in the art.
In operation, engine 200 is operated to its maximum power output without spray injection, i.e., water valve 210 is closed. In this mode of operation, air flows through air pipe 218 to nozzles 222 and 223. The air is cooled by heat exchanger 216. However, since no water is allowed through valve 210, no water is injected into the flow to high pressure compressor 204.
Once maximum power output is achieved, water injection apparatus is activated and water flows to nozzles 222 and 223. Heat exchanger 216 continues operating to reduce the temperature of the air supplied to nozzles 222 and 223. Particularly, the air flow from the eighth stage bleed 214 typically will be at about 600-650 degF. To reduce the thermal differential, or mismatch, between the bleed hot air and the water from the water reservoir, the temperature of the air from the eighth stage bleed 214 is reduced to about 250 degF. by heat exchanger 216 while maintaining the pressure of the air at about 150 psi. By maintaining the pressure at about 150 psi, the air has sufficient pressure to atomize the water.
Nozzles 222 and 223 inject water sprays 226 and 227 (illustrated schematically in
The water particles from water spray apparatus 206 provide the advantage that the temperature of the airflow at the outlet of high pressure compressor 204 (temperature T3) and the temperature of the airflow at the outlet of the combustor (temperature T41) are reduced as compared to such temperatures without the spray. Specifically, the water spray extracts heat from the hot air flowing into and through compressor 204, and by extracting such heat from the air flow, the T3 and T41 temperatures are reduced along with the required compressor power. Reducing the T3 and T41 temperatures provides the advantage that engine 200 is not T3 and T41 constrained, and therefore, engine 200 may operate at higher output levels by throttle pushing than is possible without such water spray.
That is, by injecting atomized water spray in front of high pressure compressor 204, the inlet temperature of high pressure compressor 204 is significantly reduced. Therefore, using the same compressor discharge temperature control limit, high pressure compressor 204 is able to pump more air, achieving a higher pressure ratio. This results in higher output and improved efficiency. In addition to increased power output, water spray injection as described above provides the advantage of less water consumption as compared to intercooling under the same conditions. Rather than the T3 and T41 temperature constraints, it should be understood that with the water spray configuration, the engine constraints may no longer be such temperatures, e.g., the constraints may the turbine inlet temperature T48 of the high pressure turbine and the core speed.
The above described water injection apparatus 206 may also be utilized in connection with pre-low pressure compressor water spray injection. It is believed that such pre-low pressure compressor water spray injection provides at least many of the same advantages as the intermediate, or pre-high pressure compressor, spray injection described above in connection with FIG. 9.
Rather than being originally manufactured to include injection apparatus 206, it is possible that apparatus 206 is retrofitted into existing engines. Injection apparatus 206 would be provided in kit form and include tubing 218 and 220, along with water and air manifolds 212 and 213 and water metering valve 210. Nozzles 222 and 223 also would be provided. When it is desired to provide water spray injection, nozzles 222 and 223 are installed in outer casing 224 and flow tube 218 is installed and extends from eighth stage bleed 214 to air manifold 213. Valve 210 is coupled between a water source and water manifold 212, and water manifold 212 is coupled to air manifold 213.
High pressure compressor 258 includes stator vanes which typically are not grounded to case 268. When used in combination with water spray injection, it has been found that grounding at least some of such vanes which come into contact with the water spray may be necessary. To the extent required, and using for example, graphite grease, such vanes can be grounded to case 268. That is, graphite grease may be applied to the bearing area of such vanes. For example, such graphite grease can be used at the inlet guide vane and for each down stream vane through the second stage. In operation, a portion of the grease heats and dissipates, and the graphite remains to provide a conductive path from the vane to case 268.
It also should be understood if the water can be supplied to the water spray injection nozzles under sufficient pressure, it may not be necessary to supply high pressure air to nozzles. Therefore, it is contemplated that the eight stage bleed could be eliminated if such high pressure water is available.
The temperature sensor for obtaining the temperature at the inlet of the high pressure compressor (i.e., temperature T25), is aligned with a long nozzle 282. By aligning such temperature sensor with a long nozzle 282, a more accurate temperature measurement is obtained rather than having such sensor aligned with a short nozzle 284.
Stem 292 is formed by an outer tubular conduit 298 and an inner tubular conduit 300 located within conduit 298. Air flows into nozzle 288 and through the annulus between outer conduit 298 and inner conduit 300. Water flows into nozzle 290 and through inner conduit 300. Mixing of the air and water occurs in stem portion 302 formed by a single conduit 304. An end 306 of nozzle 266 is open so that the water and air mixture can flow out from such end 306 and into the flow path.
Normally open valves 372, coupled to controls 374, are provided to enable water to drain from the water delivery line into a water drain system. Water in the water delivery line flows through a heat exchanger 376 which receives air from the eight stage bleed of high pressure compressor 258.
For frame water injection, multiple sensors 378 and control valves 380 control the supply of water to nozzles 282 and 284. Circuit 350 also includes a water accumulator 382. For inlet water injection, sensors 378 and control valve 384 control the supply of water to nozzles 282.
Letter designations in
T--temperature measurement location
P--pressure measurement location
PI--pressure indicator
N/C--normally closed
N/O--normally open
PDSW--pressure differential switch
PDI--pressure differential indicator
DRN--drain
ZS--position switch
WMV--water metering valve
PRG--purge
LVDT--linear variable differential transformer
In
Set forth below are the controls for various modes of operation of circuit 350 in connection with engine 250. In the description below, the designations Z_SPRINTON, Z_SPRINT, and Z_RAISE have the following meaning.
Z_SPRINTON=System supplier activation/sequence control for off engine H2O delivery.
Z_SPRINT=Core control logic schedule limit sequence following heat exchanger purge used for water injection, shutdown, and protective functions.
Z_RAISE=Z_SPRINT plus the manifold fill timer complete used for alarm functions.
also, an * indicates that the selected variable is tunable.
Pre-Injection Permissives/Purge Activation (AUTO or MANUAL)
1. T2>30 F.*=ON T2<27 F.*=OFF
2. Accumulator charge pressure>40 psig*
3. Operator sets Z_SPRINTON to TRUE Heat exchange purge to bypass initiated
AUTO At anytime consistent with purge time required
MANUAL on point of water injection initiation
4. Drain valves closed
Injection Permissives (Pre-Injection Permissives 1-4 Satisfied)
1. PS3 50 psi* or less below limit schedule
2. T2 regulator not active (MANUAL Only)
3. Eight stage air pressure>(PS3/4)
4. Heat exchanger purge timer complete
5. 8th stage air temperature less than 300 F.*
6. Water temperature less than 250 F.*
MANUAL Mode Sequence
1. Operator sets power to satisfy injection permissives 1-2 above and sets Z_SPRINTON=T (TRUE=ON)
2. Water pump on and heat exchange purge valve to bypass (minimum water flow).
3. Water heat exchanger purge reduce eight stage air temperature to <300 F. (Five min.*).
4. Z-SPRINT=T (TRUE=ON) SPRINT ShutOff valve opens (heat exchanger bypass diverted to engine), minimum scheduled flow to the engine
5. Flow fills manifold at minimum scheduled water flow for 60 sec.* Z_RAISE=T (TRUE=ON)
6. Operator raises SPRINT flow (0.5 gpm/sec) to maximum schedule level.
7. Operator raises power to desired level or as limited by MW, T3, T48, Ps3, XN25R3, or XN25R.
8. Power and water lowered as desired between schedule limits.
9. At PS3 60 psi below the base schedule limit sets Z_SPRINT=F and SPRINT ramp down (-2 gpm/sec) to minimum flow schedule and shutdown.
10. Activate Z_SPRINTON to OFF (FALSE=OFF) SPRINT ShutOff valve off diverts water from engine to bypass, water pump off, heat exchanger purge valve to bypass, opens the system drains and purges piping until clear and closes drains.
AUTO Mode (Permissives Satisfied)
1. Operator sets Z_SPRINTON to ON (TRUE=ON) in time to complete heat exchanger purge prior to SPRINT activation permissives.
2. Z_SPRINT=T will initiate automatically upon reaching permissive point.
3. SPRINT ShutOff valve opens (diverts water to the engine from bypass)
4. Manifold fill on minimum schedule (60 sec.*delay) Z_RAISE=T then ramps water (0.5 gpm/sec) to maximum scheduled flow.
5. Power ramps to desired level and limited by MW vs. T2 Limiter, T3, T48, Ps3, XN25R3, or XN25R.
6. Power lowered as desired to 60 psi* below the base schedule limit (T_P3BNVG) before SPRINT ramp down (-2 gpm/sec) to minimum flow schedule and shutdown occurs.
7. Activate Z-SPRINTON to OFF (FALSE=OFF) SPRINT ShutOff valve off, heat exchanger purge valve to bypass, water pump off, and open the system drains and purge piping until clear.
Alarm Requirements
Z_RAISE=TRUE (TRUE=ON) Manifold fill timer satisfied and SPRINT flowing for ALARMS.
1. Flow error (Idemand-metered)>3 gpm* for 5 seconds*-Alarm
2. 8th stage air temperature>250 F.* for 5 seconds*-Alarm
Water Shutdown Requirements
Z_SPRINT=F initiates water shutdown thru ramp down control limits and activates water shutoff.
1. Flow error (demand-metered)>6 gpm* for 10 seconds*--set Z-SPRINT=F
2. Pressure loss below 24 psi* at water demand>6 gpm*--set Z SPRINT=F
3. Pressure loss below 50 psi* at water demand>10 gpm*--set Z_SPRINT=F
4. 8th stage air temperature greater than 300 F.*--set Z_SPRINT=F
5. Eight stage air pressure<(PS3/4)--set Z_SPRINT=F
6. T2<27 F.--set Z_SPRINT=F
7. PS3 not within 60 psi* of Ps3 limit schedule--set Z_SPRINT=F
8. Any gas turbine shutdown, drop load, or step to idle--set Z_SPRINT=F (bypass water ramp down control)
9. Circuit breaker not closed--set Z_SPRINT=F (bypass water ramp down control)
HP physical speed*square root (International standard temperature/HPC exit temperature)
or,
where TSTD=518.67°CR (59°C F.).
As shown in the curve illustrated in
With respect to the droplet size, a minimum drop size at each flow rate should be produced to both reduce the residence time for complete evaporation and to hold drop sizes small enough to prevent blade erosion. Set forth below is a manner for analyzing droplet size. More specifically, and for a preliminary analysis, a 3D model of a 30°C sector of the LM-6000 booster duct is employed to determine the velocity and temperature field in the duct. No swirl is assumed at the duct inlet and the nozzle tips are located in the outer casing at the inlet of the booster duct aimed radially inward. The nozzle axis was orthogonal to the outer casing surface and the injection point was about 0.2 in. radially inward from the casing surface. The nozzle generated drop size values were taken to be the smallest values of the RR drop size, given by Equation 1. Two smaller values (i.e., 10.5 μm and 7.5 μm) were also assumed to determine the effect of drop sizes smaller than those typically generated by air atomized nozzles. The results are set forth in FIG. 17. It was assumed that 36 nozzles at 0.5 GPM each were employed, i.e., 3 to a 30°C sector.
The relation between the water flow at the inlet to the HP compressor and the stage for complete evaporation is shown in FIG. 18.
The data in
The location for complete evaporation is shown in FIG. 19. The data shows that about 20% more water injection can be evaporated at a given stage than that calculated in the preliminary analysis.
The same nozzle flow rates and initial drop sizes as those given in
The method for calculating the evaporation of the water initially deposited in the LP compressor is the same as that discussed previously. The evaporation of the fraction in drop form was calculated using a model that determines the location of complete drop evaporation. The latter was located in the LP compressor due to the small cut-off size for the undeposited flow. This cut-off size was calculated to be 13 μm at the inlet to the LP using a trajectory analysis. The results for the first four nozzles in
As a calibration for the effect of the drop cut-off size on initial deposition, if a 13 μm rather than a 10 μm cut-off size is employed for nozzle 3 in
With respect to nozzle selection and performance, the performance of selected pressure and air atomized nozzles and their effect on evaporation in the HP compressor requires knowledge of the temporal drop size distribution generated by the nozzles in the environment in which they are to be employed. The temporal size distribution has to be measured at the air density of interest. The spatial distribution of drop size, liquid volume fraction and drop velocity profile needs to be measured to calculate the temporal drop size.
A spray tunnel can be employed to measure the performance of the nozzles. The tunnel, in an exemplary test, is supplied by up to 7 lb/s air at pressures sufficient to match the booster duct air density of 0.13 lb/ft.3. The air velocity in the tunnel was varied from 45 to 75 ft/s to eliminate reverse circulation of the spray at the outer spray boundary and to keep the spray diameter small enough to avoid drop impingement on the quartz windows. The air temperature was kept below 95°C F. to eliminate the need to account for evaporation between the nozzle and measurement locations.
The radial distribution of the drop velocities in the axial direction are obtained from the measurement of the air velocities of the respective atomizing air flow rates but without water flow. The radial values of the RR drop size are multiplied by the radial values of the liquid volume fraction and axial drop velocities with the resulting product then integrated over the spray radius. After dividing by the integrated mean liquid volume fraction and axial velocity over the spray cross-section, the mean flowing RR drop size is obtained.
The air atomized nozzle performance is better than that of the pressure atomized nozzle. At 135 psig, 24 air atomized nozzles at 24 GPM total injection allows evaporation in the HP compressor while the 3000 psi pressure atomized nozzles cause 5 GPM out of the 24 GPM to break through the HP compressor. In order to evaporate 24 GPM in the HP compressor with pressure atomized nozzles at 1 GPM per nozzle, at least some nozzle configurations would have to be operated at 5000 psi. At lower water rates per nozzle, the air atomized nozzle performance improves while the pressure atomized nozzle performance decreases if the nozzle configuration is not changed. Nozzles are commercially available from FST Woodward, Zeeland, Mich., 49464.
Again, and in summary, the above described water spray injection provides the important result that increased power output can be obtained using the same compressor discharge temperature control limit. That is, by injecting atomized water spray in front of the booster and/or high pressure compressor, the inlet temperature of the high pressure compressor is significantly reduced. Therefore, using the same compressor discharge temperature control limit, the high pressure compressor is able to pump more air, achieving a higher pressure ratio. This results in higher output and improved efficiency. In addition to increased power output, the above described water spray injection provides the advantage of less water consumption as compared to intercooling under the same conditions.
While the invention has been described in terms of various specific embodiments, those skilled in the art will recognize that the invention can be practiced with modification within the spirit and scope of the claims.
Payling, Stephen R., Coleman, Robert P., Brown, Curtis L.
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